JP4955258B2 - Non-pneumatic tire - Google Patents

Description

The present invention relates to a structurally supported non-pneumatic tire or tire / wheel combination.
In particular, the present invention relates to a non-pneumatic tire that has a performance similar to that of a pneumatic tire and that can be used as a substitute for a pneumatic tire and that supports a load by a tire structural member.

  Pneumatic tires have load bearing capacity, ground impact absorption capacity and force transmission capacity (acceleration, stop, turning) and are thus favored by many vehicles, particularly bicycles, motorcycles, automobiles and trucks. These capabilities also contributed greatly to the development of automobiles and other motor vehicles. The impact absorption capability of pneumatic tires is also useful in medical equipment and electronic equipment transport carts and other applications.

  Conventional non-pneumatic tires such as solid tires, spring tires, and cushion tires do not have the superior performance of pneumatic tires. In particular, solid tires and cushion tires support the load by compressing the contact portion. This type of tire is heavy and stiff and does not have the shock absorption capability of a pneumatic tire. When the conventional non-pneumatic tire has high elasticity, the load supporting ability or durability of the pneumatic tire deteriorates. Therefore, there has been no known non-pneumatic tire widely used in place of the pneumatic tire other than a special one.

  Non-pneumatic tires / wheels having operational characteristics similar to pneumatic tires overcome the above-mentioned various disadvantages of conventional methods and are in need of development.

  The structurally supported non-pneumatic tire of the present invention includes a reinforced annular band that supports a load applied to the tire, and a plurality of load forces transmitted by tension between the reinforced annular band and the wheel or hub. Web spokes. As used herein, a tire or tire wheel refers to a structure for supporting a load solely by structural characteristics, without internal air pressure, unlike a pneumatic tire mechanism.

  In one useful embodiment of the invention, the tire or tire wheel of the invention has an outer annular band and a maximum width W extending radially from the reinforced annular band in a direction transverse to the annular band. And a plurality of web spokes having a radial height N, and means for connecting the plurality of web spokes to the wheel. The web spoke lateral profile (cross-sectional shape) is such that each web spoke has a minimum intermediate width between the outer annular band and the means for connecting the plurality of web spokes to the wheel. The plurality of web spokes have a cutaway section in a direction transverse to the annular band. The profile of the cutaway section has a height of HC and a maximum depth D of 5% or more of the radial height N and 30% or less of the maximum width W. In this profile, the angle α between the tangent line of the profile and the horizontal line at the position of the radially outermost portion and the radially innermost portion of the profile is at least 10 °. The minimum radius of curvature RR of the profile is at least 20% of the spoke height N. The annular band can further include at least one first membrane adhered to the radially inner side of the shear layer and at least one second membrane adhered to the radially outer side of the shear layer, each The membrane has a longitudinal tensile modulus that is greater than the shear modulus of the shear layer.

The above specific profile is a function of the design parameters of the spoke itself. The important geometrical elements are the tangent angle with the horizontal line, the maximum lateral depth of the profile, and the minimum radius of curvature of the profile at the radially outermost and radially innermost positions of the spokes. These geometric elements of the lateral profile are determined in a way that includes the following steps:
(a) The width W and height N of the web spoke, the radial offset Q and the lateral depth D of the profile are specified, where the depth D is not less than 5% of the radial height N and 30 W of the width W. % Or less,
(b) Calculate the value of the tangent angle α defined as the tangent between the profile and the intersection of the horizon,
(c) Compare the calculated value of the obtained tangent angle α with a predetermined minimum value, set the angle α to the larger value of the calculated value or the minimum value,
(d) Calculate the minimum curvature radius RR of the lateral profile by calculation,
(e) Compare the calculated value of the obtained radius with a predetermined minimum value,
(f) If this calculated value is larger than the minimum value, the radius RR is set to the larger calculated value.

  If the minimum radius value calculated by the above step is less than the minimum standard, the angle α is decreased until the calculated radius RR is greater than the minimum value, and steps (c) to (f) are performed. The above method can be repeated further by repeating.

  Since the structurally supported tire of the present invention does not have a cavity to accommodate pressurized air, it is not necessary to form a seal against the wheel rim to maintain the internal air pressure. Thus, structurally supported tires do not require a wheel in the pneumatic tire industry. For purposes of explanation, “wheel” and “hub” refer to any device or structure that supports the tire and is attached to the axle, and is used interchangeably herein.

  In the present invention, the reinforced annular band has an elastomer shear layer, at least one first membrane is adhered radially inside the elastomer shear layer, and at least 1 radially outward of the elastomer shear layer. Two second membranes are glued together. Each membrane has a longitudinal tensile elastic modulus larger than the shear elastic modulus of the shear layer, and when a load is applied from the outside, the tread portion in contact with the ground is basically deformed from a circular shape to coincide with the ground. On the other hand, the length of each membrane is maintained substantially constant. The relative movement of each membrane is caused by the shear force in the shear layer. Each membrane is preferably composed of a layer of embedded cord reinforcement that does not substantially extend in the elastomer coating layer.

  The shear layer is formed of an elastomeric material such as natural or synthetic rubber, polyurethane, foamed rubber and polyurethane, segmented copolyester and nylon block copolymers. The shear layer material preferably has a shear modulus of about 3 MPa to about 10 MPa. The annular band has a characteristic of bending from a normal circular shape to a contact surface such as the ground surface by an external load.

  The web spoke acts to transmit a load force by tension between the wheel and the annular band, and in particular has a function of supporting the weight of the vehicle (there is another function). The force that supports the vehicle is generated by tension in the web spokes that are not connected to the ground contact portion of the annular band. It can be said that the wheel or hub is suspended from the upper part of the tire. The web spokes preferably have a high tensile effective radial stiffness and a low compression effective radial stiffness. Due to the low compression stiffness, the web spokes attached to the ground contact portion of the annular band can bend, absorb the impact of the ground and allow the annular band to conform well to the unevenness of the ground.

  Web spokes also transmit the forces required for acceleration, stopping and turning. The placement and orientation of the web spokes can be selected to achieve the desired function. For example, in applications where relatively small circumferential forces are generated, the web spokes can be arranged radially and parallel to the axis of rotation. Web spokes perpendicular to the axis of rotation can be added alternately with web spokes aligned with the axis to provide circumferential stiffness. In another variation, web spokes that are diagonal to the tire axis are arranged to provide stiffness in both the circumferential and axial directions.

The web spokes can be curved to facilitate buckling of the web spokes at the ground contact portion of the tread. As a variant, it is also possible to apply a prestress to the web spokes during molding to bend in a specific direction.
The invention will be better understood from the following description with reference to the accompanying drawings.

“Equatorial plane” means a plane that divides a tire structure perpendicular to the tire rotation axis into two.
“Meridian plane” means a plane passing through the tire, including the rotation axis of the tire.
“Modulus, modulus” of an elastomeric material means the tensile modulus at 10% elongation as measured by ASTM standard test method D412.
The “modulus and elastic modulus” of the membrane means a value obtained by multiplying the tensile elastic modulus at 1% elongation in the circumferential direction by the effective thickness of the membrane. This modulus can be calculated by the following [Formula 1] (formula for the steel belt material of the conventional tire). This modulus is represented with a dash (').
“Shear modulus, modulus” of an elastomeric material means the elastic shear modulus and is defined as being equal to one third of the above defined tensile modulus for an elastomeric material.
“Hysteresis” means the tangent of dynamic loss (tan Δ) measured with strain, temperature, and frequency during operation. One skilled in the art will understand that the operating conditions vary depending on the specific application (eg, different loads and speeds are required for golf carts and sports cars), so the strain, temperature, and frequency must be adapted to the specific application. Like.

  FIG. 1 is an equatorial view of a structurally supported elastic tire of the present invention. “Structurally supported” means that the tire supports the load only by the structural elements of the tire without support of the gas inflation pressure. Each structure of the structurally supported elastic tire disclosed below utilizes similar basic elements (components). Accordingly, the same reference numerals are used in the drawings of the respective modifications. For the sake of clarity, the drawings are not drawn to scale and the dimensions of each element are enlarged and reduced.

  The tire 100 shown in FIG. 1 includes a tread portion 105 that contacts the ground, a reinforced annular band 110 disposed radially inward of the tread portion 105, and extends transversely across the annular band. And a web spoke 150 extending radially inward from the annular band and a mounting band 160 at the radially inner end of the web spoke. The tire 100 is fixed to the wheel 10 or the hub via the attachment band 160. “Extending in the transverse direction” means that the web spoke 150 is aligned in the axial direction or is oblique to the tire axis. “Extending radially inward” means that the web spoke 150 is in a radial plane with respect to the tire axis or is oblique to the radial plane. As will be described below, the second plurality of web spokes can also be placed on the equator plane.

  FIG. 2 is a cross-sectional view of the tire 100 and the wheel 10 at the equator plane. The reinforced annular band 110 includes an elastomeric shear layer 120, a first membrane 130 adhered to the radially innermost side of the elastomeric shear layer 120, and a second membrane adhered to the radially outermost side of the elastomeric shear layer 120. It consists of 140. The tensile stiffness of the first and second membranes 130, 140 is higher than the shear stiffness of the shear layer 120, so that the reinforced annular band 110 is shear deformed under load.

The reinforced annular band 110 supports the load applied to the tire. As shown in FIG. 1 and FIG. 5 , the load L applied to the tire rotation axis X is transmitted to the annular band 110 by the tension in the web spoke 150. The annular band 110 acts like an arch and provides circumferential compression stiffness and longitudinal bending stiffness sufficient in the tire equatorial plane to serve as a load bearing member. Under load, the annular band is deformed by the mechanism including shear deformation of the band at the contact surface C with the ground. The shear deformation capability provides a flexible ground contact surface C that acts in the same way as a pneumatic tire, with the same advantageous results as a pneumatic tire.

  With reference to FIGS. 3 and 4, the shear mechanism of the annular band 110 of the present invention compared to a rigid annular band 122 (consisting of a homogeneous material that does not substantially shear deform under load, eg, a metal ring). You will understand the advantages of. That is, in the rigid annular band 122 of FIG. 3, the pressure distribution that satisfies the equilibrium force condition and the bending moment condition is a pair of concentrated forces at both ends of the contact surface (one of which is shown in FIG. 3). Concentrate on. On the other hand, in the case of the structure of the present invention, the annular band is composed of the shear layer 120, the inner reinforcement layer 130, and the outer reinforcement layer 140 as shown in FIG. It becomes substantially uniform.

Preferred results are obtained with the annular band of the present invention when the contact pressure S is more uniform over the entire contact surface length. This is similar to a pneumatic tire and improves tire function over other non-pneumatic tires.
In a typical solid or cushion tire, the load is supported by compression of the tire structure at the contact surface, and the load bearing capacity is limited by the amount and type of material present at the contact surface. Some spring tires support the load applied to the tire by a rigid outer ring connected to a hub or wheel via an elastic spring member. The rigid outer ring does not have a shearing mechanism and therefore, as already mentioned, the rigid ring concentrates the ground reaction at both ends of the contact surface, thus transmitting the force to the ground and absorbing the ground impact Tire capacity is reduced.

Shear layer 120 comprises a layer of an elastomeric material having a shear modulus of about 3 to about 20 MPa. Suitable materials for use in this shear layer 120 include natural and synthetic rubbers, polyurethanes, foamed rubbers and polyurethanes, segmented copolyesters and nylon block copolymers.
When it rotates repeatedly under load, hysteresis loss occurs due to deformation of the shear layer 120, and heat is accumulated in the tire. Therefore, the shear layer hysteresis must be maintained below the allowable operating temperature of the material used. When using conventional tire materials (eg rubber), for example, the shear layer hysteresis should be such that the tire operating temperature is maintained at about 130 ° C. or lower for continuously used tires.

  The tread portion 105 may have no grooves or may have a plurality of longitudinal tread grooves 107 (such as grooves that form longitudinal tread ribs 109 as in the embodiment of FIG. 2). In the figure, the tread portion 105 is flat from the end portion to the support portion. This flat tread is suitable for cars and similar vehicles, but rounded treads can be used for bicycles, motorcycles and two-wheeled vehicles. One skilled in the art will appreciate that any tread pattern can be used.

  In a preferred embodiment, the first membrane 130 and the second membrane 140 comprise a cord reinforcement material that does not substantially extend in the elastomer coating layer. In the case of a tire made of an elastic material, these membranes 130 and 140 are bonded to the shear layer 120 by a cured elastomeric material. Adhering the membranes 130 and 140 to the shear layer 120 by any other securing method, such as chemically or mechanically adhering, does not depart from the scope of the present invention.

The reinforcement elements of the membranes 130, 140 can be made of any material conventionally used as a belt reinforcement for tires, such as steel, aramid monofilaments or cords, and other high modulus woven fabrics. In the case of the example tire shown, this reinforcement is four steel wire cords (4 × 0.28) with a diameter of 0.28 mm.
In the preferred embodiment, the first membrane has two reinforcing layers 131, 132, and the second membrane 140 also has two reinforcing layers 141, 142.

  In all of the illustrated variations of the present invention, each membrane has a cord reinforcement layer, but any material that satisfies the requirements of tensile stiffness, bending stiffness and compression buckling resistance required for the annular band can be used. Can be used with membranes. The membrane structure can be variously modified, for example, a uniform material (eg, a thin metal sheet), a fiber reinforced matrix, a layer having discrete reinforcing elements, or the like.

  In a first preferred embodiment, the layer 131 of the first membrane 130 has essentially parallel cords that form an angle of about 10 to about 45 degrees with the tire equatorial plane. The cords of each layer face in opposite directions. Similarly, the outer membrane 140 has layers 141 and 142 comprising essentially parallel cords that are at an angle of about 10 to about 45 ° to the equatorial plane. However, it is not always necessary that the two pairs of cords in the membrane be opposite to each other at the same angle. For example, the two pairs of cords are asymmetric with respect to the tire equatorial plane. It can also be.

In another embodiment, the cord of at least one layer of the membrane can be placed at an angle of 0 ° or approximately 0 ° with respect to the tire equatorial plane to increase the tensile stiffness of the membrane.
The cord of each layer 131, 132 and 141, 142 is typically embedded in an elastomeric coating layer having a shear modulus of about 3-20 MPa. It is preferable that the shear modulus of the covering layer is substantially the same as that of the elastomer shear layer 120 so that the deformation of the annular band is mainly performed by the shear deformation in the elastomer shear layer 120.

The deformation state of the annular band under load can be controlled by defining the relationship between the shear modulus G of the elastomer shear layer 120 and the longitudinal effective elastic modulus E ′ _membrane of the membranes 130 and 140.
The effective elastic modulus E ' _membrane of a membrane in which a conventional tire belt material is used and a reinforcing cord is arranged at an angle of at least 10 ° with respect to the equator plane can be obtained by the following formula:

(here,
E _rubber = Tensile modulus of elastomer coating material
P = Cord spacing measured at right angles to the cord direction (Distance between cord centers),
D = cord diameter,
ν = Poisson's ratio of the elastomer coating material,
α = cord angle with respect to the equatorial plane,
t = rubber thickness between cables in adjacent layers)

The tensile elastic modulus E ' _membrane of the membrane in which the reinforcing cord is arranged at an angle of 10 ° or less with respect to the equator plane can be obtained by the following formula:
E ' _membrane = E _cable ^* V ^* t _membrane (2)
(here,
E _cable = elastic modulus of cable,
V = volume fraction of cable in the membrane
t _membrane = membrane thickness)
The elastic modulus of a membrane having a matrix reinforced with a uniform material or fiber is the elastic modulus of this material or matrix.

E ' _membrane is obtained by multiplying the elastic modulus of the membrane by the effective thickness of the membrane. The deformation of the annular band under load when the ratio of E ' _membrane / G is relatively low becomes close to the deformation of the homogeneous band, and the uneven ground pressure shown in FIG. 3 is generated. Conversely, the deformation of the annular band under load when this E ' _membrane / G ratio is large enough _results mainly in the shear deformation of the shear layer, and there is little longitudinal compression or contraction of the membrane, thus [Figure 4], the contact pressure is substantially uniform.
In the present invention, the ratio of the membrane's longitudinal modulus E ' _membrane to the shear modulus G of the elastomer shear layer is at least about 100: 1, preferably at least about 1000: 1.

  The lateral profile of the tread portion 105, the first membrane 130 and the second membrane 140 of the tire shown in FIG. 2 is flat. The strain in the contact region “C” ([FIG. 1]) of the annular band is a compressive strain for the second membrane 140. As the vertical deflection of the tire increases, the contact length “C” increases, the compressive stress of the second membrane 140 exceeds the critical buckling stress, and the longitudinal buckling of the membrane occurs. Due to this buckling phenomenon, the contact pressure in the vertical direction portion of the contact area is lowered. When this membrane buckling is avoided, a uniform contact pressure can be obtained over the entire contact region. A membrane with a curved cross section is preferred when buckling occurs under load because it strongly resists buckling at the contact surface.

When the above conditions of the longitudinal elastic modulus E ' _{membrane of the membrane} and the shear modulus G of the elastomer shear layer are satisfied and the annular band is substantially deformed by shearing of the elastomer shear layer, an advantageous relationship can be established, The shear modulus G value and shear layer thickness h for each application can be determined:

(here,
P _eff = ground pressure
G = shear modulus of layer 120
h = thickness of layer 120
R = radial position relative to the rotation axis of the second membrane)

P _eff and R are design parameters selected according to the tire application. Equation (3) indicates that the product of the elastic shear modulus of the shear layer and the radial thickness of the shear layer is approximately equal to the product of the ground pressure and the radial outermost position of the second membrane. [FIG. 13] is a visual illustration of this relationship over a wide range of contact pressures and can be used to estimate the shear layer characteristic curves for various applications.

  Referring to FIG. 5, the web spoke 150 has a radial length N, an axial width W generally corresponding to the axial width of the annular band 110, and a thickness perpendicular to other dimensions. It has a substantially sheet-like element. The thickness is much smaller than the length N or W, preferably about 1-5% of the tire radius R. By doing so, the web spokes can bend under compression as shown in FIG. By thinning the web spoke, it bends at the contact surface with almost no compression resistance and no significant compressive force is applied to the load support.

  As the thickness of the web spoke increases, the web spoke provides a certain amount of compressive load bearing force to the ground plane. However, the main load transmission action of the web spoke as a whole is tension. The web spoke thickness can be selected to meet specific vehicle requirements.

  Refer to FIG. In the preferred embodiment web spoke 150 of the present invention, the use of web spokes having a substantially narrow lateral profile in the intermediate portion between the first membrane 130 and the mounting band 160 provides advantageous results. A preferred spoke 150 has a total width of W and a radial length of N. Preferred web spokes have a cutaway section transverse to the annular band. The width of the spoke in the cutaway section is inset by an axial depth D from the outside of the spoke in the axial direction, and becomes shorter. The lateral profile of each spoke is a function of a number of geometric parameters and restraining forces. Experience has shown that the method for obtaining a geometry subject to restraining forces needs to be repeated one or more times. However, a solution can be obtained without undue experimentation.

  The cutaway can be extended to the full height N of the spoke radial direction. For ease of design and manufacture, it is advantageous to provide a small area of approximately constant width adjacent to the location of the radially outer and radially inner portions of the spokes 150. This region is defined by a radial offset distance Q of 10% or less of the spoke height N. In the embodiment shown in FIG. 6, this offset distance is equal at the positions of the radially outer portion and the radially inner portion of the spoke 150. However, this is for convenience only, and the offset Q can be different above and below the spoke. Accordingly, the radial height of the cutaway section of the spoke 150 is slightly reduced and has a height HC defined as the spoke height N minus the sum of the upper and lower offsets Q. In the embodiment of FIG. 6, the vertical offset is equal. Therefore, HC = N-2Q.

The axial minimum depth D of the part with the profile must be at least 5% of the height N and not more than 30% of the spoke width W. The empirical formula for obtaining a preferred value for the axial maximum depth D of the part having the above profile is a function of the spoke height N and the offset Q as follows:

However, the predicted depth is always 30% or less of the spoke width W. The offset Q can also be zero.
The profile is not limited to a particular shape, but can be formed by a combination of straight segments joined by a portion of an arc, a parabolic arch, or a blending radius. The latter shape is a modification shown in FIG. 6 and is symmetric with respect to the intermediate height of the spoke. The straight line segment forms an angle α with the tangent and horizontal line of the profile at the radial height of the offset distance Q. The straight segments are joined by a blend radius RR having a minimum value that is at least 20% of the spoke height N. Blend radius constraints are required to avoid cutaway cross-section geometries where the selected depth D and tangent angle α can be negative segments that can negatively impact spoke performance due to the straight segments gathering at the vertices. is there.

First, the angle α is calculated, and then the lateral profile is determined by determining the blend radius RR that will join the two straight line segments. It has been found that the angle α is preferably specified from the spoke geometry as follows:

However, the minimum value of α must be at least 10 °.
Once α is determined, a preferred value for the blend radius RR can be calculated from the following relationship:

If the value of blend radius RR predicted by the selected depth D value and the calculated value of α is less than or equal to the minimum acceptable value, gradually increase the value of α until an acceptable RR value is obtained. The above operation can be repeated with a smaller size. If a solution cannot be obtained with the minimum value .alpha. Or more, the above process can be repeated with the depth D reduced.
A modification of the shape of the cutaway section is shown as a parabola as shown on the left side of FIG. In this modification, the parabola passes through points marked AA, BB, and CC , and the tangent angle α at the points AA and CC is defined as described above. Point BB defines a preferred value for depth D. That is ,

When the parabola is determined from the cutaway parameters, ie, HC, tangent angle α and depth D, the blend radius RR is determined. Since the parabolic shape cannot converge to the apex, the resulting blend radius RR value is considered large enough to ensure the correct operation of the web spoke 150.
In the presently preferred embodiment, the web spoke 150 is made of a material having a high tensile modulus, ie, a material having a tensile modulus of about 10-100 MPa. Web spokes can be reinforced as needed. In addition, the web spoke material must exhibit elastic behavior that returns to its original length after 30% strain and must exhibit a constant stress when 4% strain is applied. Furthermore, it is desirable that the tangent Δ of the material does not exceed 0.1 at the relevant operating conditions. Commercial rubber or polyurethane materials that meet these requirements can be found. The inventor has discovered that Vibrathane B836 ™ urethane from Crompton's Uniroyal Chemical Division (Middlebury, CT) is suitable for web spokes.

  Referring to FIG. 2, in one embodiment of the present invention, web spokes 150 are connected to each other by a radially inner mounting band 160. This band 160 surrounds the wheel or hub 10 for mounting the tire. The web spokes 150 are connected to each other by a boundary band 170 at their radially outer ends. This boundary band 170 connects the web spoke 150 to the annular band 110. It is convenient to mold the web spoke, mounting band 160 and boundary band 170 as a unit from a single material.

  Depending on the structural material and mounting method of the annular band 110 and the hub or wheel 10, as a variant, the web spokes can be glued directly to the annular band and wheel without the separate mounting band 160 or boundary band 170. For example, if either the annular band or wheel or hub is formed of the same material or compatible material, the tire is produced in one step by forming or molding the web spokes integrally with the annular band or wheel. be able to. In this case, the attachment band 160 and / or the boundary band 170 are integrally formed as part of the wheel or annular band. Further, the web spoke 150 can be mechanically coupled to the wheel, for example, by providing an enlarged portion at the inner end of each web spoke that engages the groove in the wheel.

  By referring to [FIG. 1] to [FIG. 6], it is possible to understand the method of supporting the load applied from the outside by the tire of the present invention. A region A that is a non-grounded portion of the annular band 110 functions in the same manner as an arch, and a tension T is applied to the web spoke 150. A load L transmitted from a vehicle (not shown) to the hub or wheel 10 and applied to the tire is basically suspended from the arch in the region A. No tension is applied to the web spokes in transition zone B and contact zone C. In the preferred embodiment, the web spokes are relatively thin and do not provide significant vertical load bearing capacity. The portion of the annular band 110 that acts as an arch will always change as the tire rotates, but it will be appreciated that the arch concept helps to understand this mechanism.

  By using web spokes with high tensile stiffness but low compression stiffness, substantially only tensile load support is obtained. The web spokes can be curved to facilitate buckling in the contact area. In a modified example, the web spokes can be curved and then straightened by thermal contraction during cooling to provide buckling.

  The web spoke 150 must withstand the torsion between the annular band 110 and the wheel 10, for example when torque is applied to the wheel. In addition, the web spoke 150 must withstand lateral deflection, for example when turning or cornering. Radial-Axis plane web spokes 150, i.e. aligned in both radial and axial directions, are highly resistant to axial forces, but resist circumferential torques, especially when extended radially. I understand that it is difficult to do. For certain vehicles and applications, such as vehicles and applications that generate relatively small acceleration forces, a web spoke assembly with relatively short spokes aligned in the radial direction is suitable.

  For applications where a large torque is expected, the arrangement and structure shown in FIGS. 7 to 9 are suitable. In FIG. 7, two web spokes 150 are joined at the center to form X, and arranged in a pattern in which X is repeated as viewed from the axial direction. In FIG. 8, web spokes are arranged in a zigzag pattern with respect to the radial direction. The web spokes in FIG. 9 are arranged so that adjacent web spokes face away from the axial direction of the zigzag pattern. In these variations, each direction provides a component that resists both radial and circumferential forces, and thus a resistance to torque is applied while retaining components that resist radial and lateral forces. The orientation angle can be selected depending on the number of web spokes used and the spacing between two adjacent web spokes.

Other arrangements are possible. As shown in FIG. 10, the web spokes can be arranged in a mountain shape or a V shape when viewed in the radial direction. In another variation, as shown in FIG. 11, it changes alternately between spokes 150 and the spokes 15 in alignment with the circumferential direction in alignment with the direction of web spokes axially adjacent. However, the modified examples of [FIG. 10] and [FIG. 11] are less preferable than the arrangements of [FIG. 7] to [FIG. 9] because it is difficult to receive the buckling of the web spoke in the contact area.
By varying the arrangement of the web spokes, the vertical, lateral and torsional stiffness of the tire can be adjusted independently of the contact pressure and further independently of each other.

Vertical stiffness has a significant effect on the deflection durability of a tire under load. The vertical stiffness of a tire is strongly influenced by the reaction of the part of the tire that is not in contact with the ground ("counterdeflect" of the tire). [FIG. 12] exaggerates this phenomenon. When a load L is applied to the tire, it bends by the amount of f, and the part in the ground contact surface is deformed into the shape of the ground, so that the ground contact area becomes C. It should be noted that in FIG. 12, for the sake of explanation, the standard frame is shown by moving the ground upward from the axis so that the tire axis X is maintained at a fixed position. Tire is an elastic member, the vertical deflection f is proportional to the load L, it is possible to determine the vertical stiffness K _v of the tire. Since the annular band 110 (conceptual diagram) constrained by a membrane (not shown) tries to maintain a certain length, the non-contact tire part shifts, that is, the contact surface as shown by the broken line in the figure. Counterdeflects away from C. Since the reverse deflection amount λ is also proportional to the load L, the reverse deflection stiffness K _λ can also be obtained. This reverse deflection stiffness Kλ is mainly related to the circumferential compression stiffness and the state when the web spokes that are not in contact with the ground are subjected to a load, and is somewhat related to the lateral and longitudinal bending of the annular band.

  This reverse deflection can be measured accurately directly from the tire under load F by fixing the axis and measuring the deflection f of the tire at the contact surface and the deflection of the tread surface opposite the contact surface. The reverse deflection stiffness is obtained by dividing the load F by the reverse deflection amount λ.

In practice, the reverse deflection stiffness K _λ substantially controls the vertical stiffness of the tire (and hence the deflection under the load of the tire axle). As can be seen from FIG. 12, the reverse bending stiffness K _lambda determines the contact surface length. When the reverse deflection stiffness is small, the annular band 110 moves vertically under load, and the load resistance decreases due to the deflection. Therefore, a tire having a large reverse deflection stiffness has relatively little reverse deflection and a long contact surface.

[Figure 14] is a visual indication of the relationship between the stiffness K _lambda counter-bending perpendicular stiffness of the tire. [FIG. 14] shows that the vertical stiffness and the contact pressure obtained in the present invention are independent. This is a design freedom that cannot be obtained with pneumatic tires. Generally, the reverse deflection stiffness per unit contact width of a contracted pneumatic tire is 0.1 DaN / mm ² or less, whereas the reverse deflection stiffness per unit contact width of the tire of the present invention is about 0.1 DaN / mm ² or more. is there.

By using [FIG. 14] and [FIG. 13] in combination, it is possible to select starting design parameters suitable for each application. By selecting the contact pressure, the vertical load, and the contact surface using [FIG. 13], the vertical stiffness characteristics of the tire can be determined using [FIG. 14]. The designer can determine the structure to achieve stiffness with using the approximate target value of stiffness K _lambda reverse deflection obtained in [13], a known analysis tools, such as finite element analysis. The design parameters will be confirmed in subsequent work (tire manufacture and testing).

For example, when designing a tire for a passenger car, the designer can select a contact pressure P _eff of 1.5 to 2.5 DaN / cm ² and a tire size radius R of about 335 mm. By multiplying these values, a “shear layer factor” of 50.25 to 83.75 DaN / cm can be determined, which can be used to determine the thickness and shear modulus of the shear layer material. In this case, with a shear modulus of about 3 MPa to about 10 MPa, the thickness h of the elastomer shear layer is at least 5 mm, preferably about 10 mm to about 20 mm.

  Further, in the pneumatic tire, the tire contact pressure and the tire stiffness are related to the tire pressure. In the present invention, these are independent of each other. Therefore, it is possible to design a tire having a high contact pressure P but a relatively low stiffness. This is advantageous for producing tires that maintain load carrying capacity and have low weight and rotational resistance.

Conversely bending stiffness K _lambda can be modified in various ways. Design parameters that can be used to adjust this stiffness include web spoke modulus, web spoke length, web spoke curvature, web thickness, compression modulus of the membrane of the annular band, shear layer thickness, tire diameter. And the width of the annular band.
By adjusting the vertical stiffness, the load bearing capacity of a given tire can be optimized. Alternatively, the vertical stiffness can be adjusted to reduce the thickness of the annular band to reduce the contact pressure or reduce the tire weight while maintaining the vertical stiffness at a predetermined level.

The vertical stiffness of the tire of the present invention is also influenced by the centripetal force effect applied to the annular band and the sidewall portion. This centripetal force occurs as the tire speed increases during rotation. In contrast to conventional radial tires, centripetal force increases the tire operating temperature, but in contrast to this, the tires of the present invention provide completely unexpected and advantageous results. When the tire of the present invention rotates under load, the annular band tends to expand in the circumferential direction due to centripetal force, and further induces tensile stress on the web spoke. A radially stiff web spoke resists this centripetal force at the non-contact portion of the tire (area A in [FIG. 1]), thereby creating an overall upward force that increases the effective vertical stiffness of the tire. Further, the radial deflection of the tire with respect to the stationary state (when not rotating) is reduced. This result becomes significant when the ratio of the longitudinal stiffness (2E ' _membrane ) of the band at the tire equatorial plane to the effective stiffness of the sidewall portion during tension is 100: 1 or less.

  It will be understood from the contents of the present specification that many variations other than those described above are possible for those skilled in the art. Variations and other variations that fall within the scope of the claims are within the scope of the present invention.

The conceptual diagram in the equatorial plane of the tire of this invention under load. Sectional drawing which cut the tire of this invention in the meridian plane. The conceptual diagram which illustrated the grounding reaction in the case of the homogeneous band of the comparative example which does not show a shear deformation. The conceptual diagram which illustrated the grounding reaction in the case of the annular band of this invention. The conceptual diagram in the meridian plane of this invention tire which added the load which shows a predetermined | prescribed reference | standard dimension in order to demonstrate a load support mechanism. Conceptual diagram of the tire of the present invention showing the lateral profile of the web spokes cut at the meridian plane Sectional drawing seen in the equatorial plane which shows X pattern arrangement | positioning of a web spoke. The figure seen in the equatorial plane which shows the zigzag pattern arrangement | positioning of a web spoke. The figure which looked at the oblique axis pattern arrangement | positioning of the web spoke from the radial direction toward the rotating axis. The figure which looked at the mountain-shaped arrangement | positioning of the web spoke from the radial direction toward the rotation axis. The figure which looked at the arrangement | positioning by which the web spoke was alternately aligned with the circumferential direction and the axial direction from the radial direction toward the rotating axis. Conceptual diagram of reverse deflection stiffness as seen on the tire equator. The figure which showed visually the relationship of the contact surface of this invention tire, a contact pressure, and a perpendicular load. The figure which showed visually the relationship between the contact pressure of this invention tire, a vertical direction stiffness, and a reverse bending stiffness.

Claims (19)

A structurally supported tire,
An outer annular band, a plurality of web spokes having a maximum width and a radial height extending radially inwardly and transversely from the outer annular band, and means for connecting the plurality of web spokes to the wheel. And
The annular band includes a shear layer, at least one first membrane adhered radially inward of the shear layer, and at least one second membrane adhered radially outward of the shear layer, each The membrane has a longitudinal tensile modulus greater than the shear modulus of the shear layer,
The plurality of web spokes have a cutaway section in a direction transverse to the band, and the profile of the cutaway section has a constant cutaway section height and a radial height of the web spoke. A cutaway cross section maximum depth of 5% or more and 30% or less of the maximum width of the web spoke ,
In the profile, the tangent angle α formed by the tangent line and the horizontal line of the profile at the position of the radially outermost portion and the radially innermost portion of the profile is at least 10 degrees,
Tire minimum radius of curvature of the profile is characterized in that at least 20% of the radial height of the web spokes. A tire according to claim 1, wherein the cutaway section is radially offset from the means for connecting the outer annular band and the web spoke to the wheel, the radial offset being no more than 10% of the height. The tire according to claim 2, wherein the maximum cutaway cross section depth is not more than the value of the following formula:

(Where N is equal to the above height and Q is the above radial offset) The tire according to claim 1, wherein the tangent angle is not less than 10 ° and not more than a value of the following formula:

(Where HC is equal to the radial height of the cutaway section and D is the depth) The tire according to claim 1, wherein the radius RR is 20% or more of the radial height N and not more than a value of the following formula:

(Where HC is equal to the radial height of the cutaway section, D is the depth, and α is the tangent angle)   The tire according to claim 1, further comprising a tread portion disposed radially outward of the annular band.   The tire of claim 1 wherein the means for connecting the plurality of web spokes to the wheel comprises a mounting band connecting the radially inner ends of the web spokes together.   The tire of claim 1, wherein the plurality of web spokes further comprises a radially outer band that connects the radially outer ends of the web spokes together.   The tire according to claim 1, wherein each of the web spokes is oriented in a direction parallel to the axial direction.   The tire according to claim 1, wherein the ratio of one longitudinal tensile modulus of the membrane to the shear modulus of the shear layer is at least 100: 1.   The tire of claim 1, wherein the product of the shear modulus of the shear layer and the radial thickness of the shear layer is approximately equal to the product of the contact pressure and the outermost radial position of the second membrane. The first and second membranes each comprise a substantially non-stretchable cord reinforcement layer embedded in an elastomeric coating layer having a shear modulus equal to at least the shear modulus of the shear layer. Tires.   The cutaway is defined by a parabola having a tangent angle α of at least 10 ° at radially outermost and radially innermost positions of the profile, the parabola passing through an axial position corresponding to a maximum depth. The tire according to 1. How to determine the web spoke lateral profile, including the following steps:
(a) Identify web spoke width and height, radial offset, and profile cutaway cross-sectional depth, with depth not less than 5% of radial height and not more than 30% of width. ,
(b) Calculate the tangent angle α defined by the tangent and horizontal lines of the profile,
(c) Compare the value of the tangent angle α obtained by calculation with the specified minimum value, set the angle to the larger value of the calculated value or the minimum value,
(d) Calculate the minimum radius of curvature of the lateral profile by calculation,
(e) Compare the calculated value with the specified minimum radius value,
(f) If the calculated value is larger than the minimum value, set the radius to the larger calculated value. The method according to claim 14, wherein the calculated value of the angle α is equal to the value of the following equation:

(Where HC is equal to the radial height of the cutaway section and D is the depth)   The method according to claim 14, wherein the minimum radius of curvature value is 20% of the radial height N of the web spoke. 15. The method of claim 14, wherein the radius is at least 20% of the radial height and not more than the value of the following formula:

(Where HC is equal to the radial height of the cutaway section, D is the depth, and α is the tangent angle)   The method according to claim 14, wherein the minimum value of the tangent angle α is 10 °. The method according to claim 14, wherein when the radius is smaller than the minimum value, the steps (c) to (f) are repeated to reduce the value of the tangent angle α .

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